US20220333568A1 - High-Pressure Fuel Pump - Google Patents

High-Pressure Fuel Pump Download PDF

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Publication number
US20220333568A1
US20220333568A1 US17/633,093 US202017633093A US2022333568A1 US 20220333568 A1 US20220333568 A1 US 20220333568A1 US 202017633093 A US202017633093 A US 202017633093A US 2022333568 A1 US2022333568 A1 US 2022333568A1
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United States
Prior art keywords
diaphragms
fuel pump
pressure fuel
section
diaphragm
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US17/633,093
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English (en)
Inventor
Stefan Kolb
Daniel Beckmann
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Assigned to ROBERT BOSCH GMBH reassignment ROBERT BOSCH GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: Beckmann, Daniel, KOLB, STEFAN
Publication of US20220333568A1 publication Critical patent/US20220333568A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
    • F02M37/0011—Constructional details; Manufacturing or assembly of elements of fuel systems; Materials therefor
    • F02M37/0041—Means for damping pressure pulsations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/48—Assembling; Disassembling; Replacing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F04B11/0008—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators
    • F04B11/0016—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators with a fluid spring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F04B9/042—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being cams
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
    • F02M2200/8023—Fuel injection apparatus manufacture, repair or assembly the assembly involving use of quick-acting mechanisms, e.g. clips
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
    • F02M2200/8084—Fuel injection apparatus manufacture, repair or assembly involving welding or soldering
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B23/00—Pumping installations or systems
    • F04B23/04—Combinations of two or more pumps

Definitions

  • the invention relates to a high-pressure fuel pump according to the preamble of claim 1 .
  • DE 10 2015 219 537 A1 describes a high-pressure fuel pump that is used in a fuel system of an internal combustion engine.
  • Said high-pressure fuel pump is used to compress the fuel to a very high pressure, in order for said fuel to then be injected directly into the combustion chambers of the internal combustion engine by means of injectors.
  • the known high-pressure fuel pump is a piston pump, the delivery rate of which can be influenced by an inlet-side flow rate control valve. This results in pressure pulsations being generated in an inlet-side low-pressure region, which pressure pulsations are reduced by means of a pressure pulsation damper arranged there.
  • Said pressure pulsation damper comprises a diaphragm cell with, for example, two diaphragms arranged substantially approximately parallel to one another, which diaphragms are welded to one another at the edge.
  • the diaphragm cell In a receiving space of a pump housing, the diaphragm cell is clamped between a holding ring and a spring.
  • the high-pressure fuel pump according to the invention comprises a low-pressure region and a pressure pulsation damper arranged in the low-pressure region.
  • the expression “low-pressure region” refers to an inlet-side region upstream of the compression of the fuel.
  • the pressure pulsation damper comprises at least one diaphragm cell and is arranged in a receiving space which is delimited, for example, by a housing cover of the high-pressure fuel pump.
  • the diaphragm cell preferably has two diaphragms, which may for example be arranged mirror-symmetrically with respect to one another, and between which an interior space of the pressure pulsation damper is formed, which interior space is delimited by said diaphragms.
  • the interior space may for example be filled with a compressible gaseous fluid (for example air or nitrogen), such that, in the presence of particular ambient conditions, a particular pressure prevails in the interior space.
  • a holding device for holding the diaphragm cell in the receiving space.
  • said holding device comprises a connecting section which is fixedly connected both in an axial direction and in a radial direction to the pump housing and which in particular is fastened both in an axial direction and in a radial direction to an inner lateral surface that delimits the receiving space.
  • the holding ring that was hitherto present and the spring that was hitherto present are omitted.
  • the diaphragm cell is fastened both in an axial direction and in a radial direction to the pump housing by means of the holding device and the connecting section thereof.
  • an axial and a radial direction can be referred to in the present case because the diaphragm cell is conventionally a part that is, at least in certain sections and at least substantially, rotationally symmetrical.
  • the invention has the effect that the hitherto provided components of holding ring and spring can be omitted, whereby costs can be saved and the required axial extent (structural height) is reduced.
  • the spring variance is also eliminated, and costs are further reduced owing to the possible omission of further interface components. Since it is no longer necessary for a spring to be supported, for example, on a housing cover that delimits the receiving space, the specification for this is eliminated, such that the cover can also be of simpler form and thus less expensive.
  • a similar situation applies to the design of a housing surface on which the holding ring hitherto had to be supported.
  • the connecting section is fixed to the inner lateral surface with an interference fit and/or is welded to the inner lateral surface.
  • These are particularly simple and reliable and durable types of connection. If the inner lateral surface is that of a housing cover, the diaphragm cell can be easily pre-installed in the housing cover, whereby a yet further cost saving is possible.
  • the two diaphragms are welded to one another in the region of a radially outer edge by means of a weld line extending in a circumferential direction, and that the holding device has at least two clamping sections, between which the two diaphragms are clamped in a region radially to the inside of the weld line.
  • the weld line is relieved of load and thus the durability of the diaphragm cell is improved.
  • the relief of load is based on the fact that the movements of the diaphragms are kept away from the weld line or are at least reduced, such that the bending load on the welded connection is reduced.
  • At least one of the clamping sections is formed as a single piece with the connecting section. This reduces the number of parts that need to be handled, whereby the assembly process is simplified, and ultimately a yet further cost saving is possible.
  • clamping sections are welded to one another.
  • a very enduringly stable unit is created in this way.
  • clamping sections are clipped to one another. This can be implemented inexpensively.
  • the connecting section is formed integrally on the diaphragm cell. A particularly stable and easily installable unit is created in this way.
  • the two diaphragms are welded to one another in the region of an edge of at least one of the two diaphragms by means of a weld line extending in a circumferential direction, wherein, between the weld line and an interior space formed between the two diaphragms, a region is present in which the two diaphragms lie frictionally against one another at least in certain sections.
  • the weld line is relieved of load with regard to the movements of the diaphragms not by clamping radially to the inside but by frictional engagement between the two diaphragms that is present “radially” to the inside of the weld line. In this way, the relative movements of the two diaphragms during operation are at least substantially kept away from the weld line.
  • a bend is present between the weld line and the interior space formed between the two diaphragms.
  • a bend is to be understood as meaning that the two diaphragms are bent, that is to say a type of common collar-like and axially extending section is formed.
  • the bend has an angle of preferably approximately 90° and has a radius, wherein the radius of the inner diaphragm in the region of the bend is smaller than the radius of the outer diaphragm in the region of the bend.
  • Such a bend likewise reduces bending loads that act on the weld line during operation.
  • FIG. 1 is a schematic illustration of a fuel system of an internal combustion engine with a high-pressure fuel pump
  • FIG. 2 shows a partial longitudinal section through a region of the high-pressure fuel pump from FIG. 1 in a first embodiment
  • FIG. 3 shows a detail III from FIG. 2 ;
  • FIG. 4 is an illustration similar to FIG. 3 for a high-pressure fuel pump in a second embodiment
  • FIG. 5 shows a region of the high-pressure fuel pump from FIG. 4 in a modified embodiment
  • FIG. 6 is an illustration similar to FIG. 5 for a yet further modified embodiment.
  • a fuel system is denoted, overall, by the reference designation 10 .
  • Said fuel system serves, in a very simplified schematic illustration, for providing fuel for an internal combustion engine (not illustrated in any more detail).
  • a flow rate control valve 24 which can be actuated by an electromagnetic actuating device 22 , and to a working chamber 26 of a high-pressure fuel pump 28 , for example with an admission pressure, provided by the predelivery pump 16 , of 4-8 bar, in particular approximately 6 bar.
  • the flow rate control valve 24 may be a positively openable inlet valve of the high-pressure fuel pump 28 .
  • a piston 30 of the high-pressure fuel pump 28 can be moved vertically in the drawing by means of a cam disk 32 .
  • a cam disk 32 Arranged hydraulically between the working chamber 26 and an outlet 34 of the high-pressure fuel pump 28 are an outlet valve 36 , shown as a spring-loaded check valve, and a pressure-limiting valve 38 , likewise shown as a spring-loaded check valve.
  • the outlet 34 is connected via a high-pressure line 40 to a high-pressure accumulator 42 (“common rail”).
  • the predelivery pump 16 delivers fuel from the fuel tank 12 into the low-pressure line 18 .
  • the flow rate control valve 24 can be closed and opened in a manner dependent on a respective demand for fuel.
  • the fuel quantity that is delivered to the high-pressure accumulator 42 is influenced in this way.
  • pressure pulsations occur in several sections of the fuel system 10 , in particular also upstream of the working chamber 26 , that is to say in a low-pressure region 43 of the high-pressure fuel pump 28 or of the fuel system 10 .
  • a pressure pulsation damper 44 is arranged there in order to dampen said pressure pulsations.
  • the high-pressure fuel pump 28 comprises a pump housing 46 , which has a substantially cylindrical or rotationally symmetrical shape. In the upper region of the pump housing 42 in FIG. 2 , this has an end side 48 , onto which there is placed a hood-like housing cover 50 that is connected in fluid-tight fashion, for example welded, to the pump housing 46 . Between the end side 48 and the housing cover 50 , there is formed a fluid chamber 52 that is connected via a channel 54 to the low-pressure region 43 .
  • the abovementioned pressure pulsation damper 44 which in the present case comprises a diaphragm cell 56 , is arranged in the fluid chamber 52 .
  • the fluid chamber 52 can also be referred to as receiving space.
  • the diaphragm cell 56 in turn comprises two diaphragms 58 a and 58 b , which in a central region are substantially identical and arranged mirror-symmetrically and which, in plan view, have a substantially circular contour and are of rotationally symmetrical form.
  • the two diaphragms 58 a and 58 b are welded to one another in fluid-tight fashion by means of a weld line 60 at their radially outer edge.
  • the diaphragm cell 56 is held in the fluid chamber 52 by means of a holding device 62 .
  • the holding device 62 will be discussed in more detail further below.
  • An interior space 64 is formed between the two diaphragms 58 a and 58 b . Said interior space is thus delimited by the two diaphragms 58 a and 58 b .
  • This interior space 64 is filled with a gas, for example nitrogen or air, namely at a specific pressure.
  • the holding device 62 comprises a connecting section 66 , which in the present case is formed integrally on the upper diaphragm 58 a and thus on the diaphragm cell 56 .
  • the upper diaphragm 58 a is configured as follows (see also FIG. 3 ): a working region of the diaphragm 58 a is formed by an abovementioned central region 68 , in which bead-like formations (without reference designation) are present which run in encircling fashion in a circumferential direction and which allow a movement of the diaphragm 58 a in an axial direction 70 .
  • the diaphragms 58 a and 58 b have a substantially circular contour and are of rotationally symmetrical form, said axial direction 70 can be defined. There is a corresponding radial direction orthogonal with respect to said axial direction.
  • the abovementioned function of the damping of pressure pulsations is achieved by way of the abovementioned movement of the central region 68 of the diaphragm 58 a and of the corresponding central region (without reference designation) of the diaphragm 58 b.
  • the diaphragm 58 a Radially outside the central region 68 , the diaphragm 58 a has a radially outwardly extending flat first section 74 , which runs in encircling fashion in a circumferential direction. At the radially outer edge thereof, a bend 76 is present by way of which the diaphragm 58 a is bent downward through, for example, 90° in the present case.
  • the bend 76 has a radius R.
  • a second section 78 running in encircling fashion in a circumferential direction extends downward in an axial direction, in the form of a cylindrical collar, from the bend 76 .
  • a third section 80 which runs in encircling fashion in a circumferential direction, specifically obliquely outward at an angle of, for example, approximately 45° in the present case.
  • Distributed uniformly in a circumferential direction in the third section 80 is a multiplicity of openings 82 through which fuel can flow during operation.
  • On the third section 80 there is integrally formed a fourth section which, in the present case, runs for example in encircling fashion in a circumferential direction and which extends in a straight manner in an axial direction 70 , downward in FIG. 3 , and which is thus likewise configured in the form of a cylindrical collar.
  • the diaphragm 58 b Radially outside its central region 68 , the diaphragm 58 b has a likewise radially outwardly extending flat first section 86 running in encircling fashion in a circumferential direction. Present at the radially outer edge thereof is a bend 88 by way of which the diaphragm 58 b is bent downward through, for example, 90° in the present case.
  • the bend 88 has a radius r.
  • a second section 90 running in encircling fashion in a circumferential direction extends downward in an axial direction, in the form of a cylindrical collar, from the bend 88 .
  • the second section 90 of the diaphragm 58 b forms a radially inner section
  • the second section 78 of the diaphragm 58 a forms a radially outer section.
  • the second section 90 of the diaphragm 58 b however extends less far in the axial direction 70 than the second section 78 of the diaphragm 58 a.
  • said diaphragm is welded to the second section 78 of the diaphragm 58 a by means of the abovementioned weld line 60 .
  • the second and radially inner section 90 of the diaphragm 58 b is received with an interference fit in the second and radially outer section 78 of the diaphragm 58 a .
  • the bend 76 and the bend 88 , and the first section 74 and the first section 86 are joined together so as to lie frictionally against one another. It is achieved in this way that the movement of the central regions 68 of the two diaphragms 58 a and 58 b are at least substantially kept away from the weld line 60 .
  • the fourth section 84 of the diaphragm 58 a is fixed by way of an interference fit to an inner lateral surface 92 of the housing cover 50 .
  • said fourth section is additionally or alternatively welded to the inner lateral surface.
  • the connecting section 66 which in the present case is formed in particular by the bend 76 , the second section 78 , the third section 80 and the fourth section 84 , of the holding device 62 is fixedly connected to the housing cover 50 and thus to the pump housing 46 both in the axial direction 70 and in the radial direction 72 .
  • the diaphragm cell 56 is thus held immovably and captively in the housing cover 50 .
  • the two diaphragms 58 a and 58 b are of identical design with respect to one another, and the weld line 60 is present at the projecting edge of the first section 74 of the diaphragm 58 a and of the second section 86 of the diaphragm 58 b .
  • the holding device 62 has two resilient clamping sections 94 and 96 which are preloaded toward one another and between which the first section 74 of the diaphragm 58 a and the first section 86 of the diaphragm 58 b are clamped.
  • the two diaphragms 58 a and 58 b are thus clamped in a region radially to the inside of the weld line 60 .
  • the upper clamping section 94 in FIG. 4 is formed at the upper edge of the second section 78 of the holding device 62 in FIG. 4 , and is thus formed integrally with the connecting section 66 , which is formed in the present case predominantly by the second section 78 , the third section 80 and the fourth section 84 .
  • the lower clamping section 96 in FIG. 4 is fastened to the second connecting section 78 in a manner not illustrated in any more detail in FIG. 4 .
  • the lower clamping section 96 may be fastened to the second section 78 by means of a clip connection with latching action, as can be seen from FIG. 5 .
  • openings 98 are present into which resilient latching lugs 100 of the lower clamping section 96 can latch.
  • the lower clamping section 96 may also simply be welded to the second section 78 (weld line 102 ), as can be seen from FIG. 6 . In both cases, it must be ensured that the two clamping sections 94 and 96 are axially preloaded relative to one another such that a sufficiently strong clamping force is exerted on the first sections 74 and 86 of the diaphragms 58 a and 58 b.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Reciprocating Pumps (AREA)
  • Fuel-Injection Apparatus (AREA)
US17/633,093 2019-08-09 2020-07-22 High-Pressure Fuel Pump Abandoned US20220333568A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102019212005.9 2019-08-09
DE102019212005.9A DE102019212005A1 (de) 2019-08-09 2019-08-09 Kraftstoff-Hochdruckpumpe
PCT/EP2020/070631 WO2021028169A1 (fr) 2019-08-09 2020-07-22 Pompe à carburant à haute pression

Publications (1)

Publication Number Publication Date
US20220333568A1 true US20220333568A1 (en) 2022-10-20

Family

ID=71784037

Family Applications (1)

Application Number Title Priority Date Filing Date
US17/633,093 Abandoned US20220333568A1 (en) 2019-08-09 2020-07-22 High-Pressure Fuel Pump

Country Status (7)

Country Link
US (1) US20220333568A1 (fr)
EP (1) EP4010581A1 (fr)
JP (1) JP2022543692A (fr)
KR (1) KR20220043928A (fr)
CN (1) CN114555932A (fr)
DE (1) DE102019212005A1 (fr)
WO (1) WO2021028169A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN117716382A (zh) 2022-07-14 2024-03-15 三菱电机株式会社 接受订货辅助装置、接受订货辅助方法、工厂系统、接受订货方法和接受订货辅助系统

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US5772288A (en) * 1996-06-11 1998-06-30 Accuride Corporation Vehicle wheel
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US20080175735A1 (en) * 2007-01-10 2008-07-24 Stanadyne Corporation Inlet pressure attenuator for single plunger fuel pump
US8757212B2 (en) * 2008-02-18 2014-06-24 Continental Teves Ag & Co. Ohg Pulsation damping capsule
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JP5002523B2 (ja) * 2008-04-25 2012-08-15 日立オートモティブシステムズ株式会社 燃料の圧力脈動低減機構、及びそれを備えた内燃機関の高圧燃料供給ポンプ
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JP2004138071A (ja) * 2002-10-19 2004-05-13 Robert Bosch Gmbh 流体システム内の圧力脈動を減衰するための装置
US20080175735A1 (en) * 2007-01-10 2008-07-24 Stanadyne Corporation Inlet pressure attenuator for single plunger fuel pump
US8757212B2 (en) * 2008-02-18 2014-06-24 Continental Teves Ag & Co. Ohg Pulsation damping capsule
US20160305431A1 (en) * 2013-12-01 2016-10-20 Aspen Compressor, Llc Compact low noise rotary compressor
US20160298581A1 (en) * 2015-04-09 2016-10-13 Hyundai Kefico Corporation Damper assembly of high-pressure fuel pump

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Title
Machine Translation of Japanese Patent JP 2004138071 A to Rembold, retrieved from espacenet on 10/18/2023 (Year: 2023) *
Machine Translation of Japanese Patent JP 2012184757 A to Denso, retrieved from espacenet on 10/19/2023 (Year: 2023) *

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JP2022543692A (ja) 2022-10-13
EP4010581A1 (fr) 2022-06-15
CN114555932A (zh) 2022-05-27
KR20220043928A (ko) 2022-04-05
WO2021028169A1 (fr) 2021-02-18
DE102019212005A1 (de) 2021-02-11

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